Machine for the production of glass bottles or the like

ABSTRACT

A press-and-blow bottle-making machine wherein several neck rings orbit about a vertical axis and wherein each neck ring is moved by a separate motor so that the length of intervals during which the rings dwell at various treating stations and the speed of rings during travel between the stations can be selected as a function of the time required for treatment of workpieces carried by the neck rings at or between the stations.

United States Patent Becker Feb. 22, 1972 [5.4] MACHINE FOR THE PRODUCTION OF GLASS BOTTLES OR THE LIKE [72] inventor: Kurt Becker, Obernkirchen, Germany [73] Assignee: Hermann Heye, Obemkirchen, Germany [22] Filed: Dec. 26, 1968 211 App1.No.: 786,899

[30] Foreign Application Priority Data Jan. 9, 1968 Germany ..H 65000 [52] [15. CL ..65/l58, 18/5, 65/229. 65/241, 65/251. 65/320 [51} Int. Cl. ..C03b 9/40 [58] Field ofSearch ..65/82, 229, 237, 240, 250, 65/241, 242, 251, 252, 248, 320, 158, 160; 18/5,

[56] References Cited UNITED STATES PATENTS 3,069,860 12/1962 Colchagoffet a1 .12....65/241 744,008 1 1/ 1903 Proeger ..65/ 229 805,027 11/1905 Pawling et aL. ....65/239 1,693,843 12/1928 Jaeger ....65/229 2,722,084 11/1955 Winder ....65/237 2,757,484 8/1956 Winder ....65/237 3,142,552 7/1964 Martin ..65/229 Primary Examiner-S. Leon Bashore Assistant Examiner-Robert L. Lindsay, Jr. Att0rneyMichae1 S. Striker [57] ABSTRACT 48 Clairns, 26 Drawing Figures PAIENIEUFB22|912 3644.1 1.1

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INVENTOR 16 2 Km BECKER PRODUCTION OF GLASS BOTTLES OR THE LIKE BACKGROUND OF THE INVENTION 7 The present invention relates to a process for the production of hollow articles and to a machine which can be utilized in the practice of such process. More particularly, the invention relates to a process and machine for automatic production of bottles or analogous hollow articles consisting of vitreous or synthetic plastic material by the press-and-blow method.

Presently known press-and-blow machines produce hollow articles in a series of stages. In the first stage, a blank or gob is deformed in a stationary blank mold. In the-next-following step, the resulting parison is removed from the blank mold and is reheated on its way to a stationary blow mold wherein the parison is converted into a finished article. In a further step, the finished article is removed from the stationary blow mold and is transported to a conveyor which advances the article to a cooling furnace. A drawback of such machines is that the operation which requires the longest interval of time determines the intervals during which the parisons and finished articles dwell at the respective stations. Thus, the'reheating of parisons and their transport to the stationary blow mold takes up the same amount of time as the conversion of parisons into finished articles in response to introduction of blowing medium into parisons which are accommodated in the blow mold. This means that the molds are not used to maximum capacity because a machine can convert a gob into a parison more rapidly than a parison into a finished article or vice versa. In other words, in such conventional press-and-blow machines, only that part or that group of parts which requires the longest interval of time to perform its function during a cycle is used to capacity because such part or such group'of parts determines the operating speed of the entire machine.

SUMMARY OF THE INVENTION It is an object of my invention to provide a novel process for the production of hollow articles in accordance with the pressand-blow method.

Another object of the invention is to provide a process according to which bottles or analogous hollow articles of vitreous or synthetic plastic material can be produced more economically and more rapidly than in accordance with presently known processes.

A further object is to provide a press-and -blow machine wherein the transformation of blanks into hollow articles is carried out with a minimum of delay and with maximum utilization of parts at each of the several stations at which the blanks are treated to be converted into bottles or the like.

An additional object of the invention is to provide the machine with novel and improved transporting means for blanks and hollow articles.

A concomitant object of the invention is to provide a machine wherein the blanks are caused to dwell at several stations during conversion into hollow articles and wherein the duration of dwell at a particular station does'not depend on the nature of treatment of the other station or stations.

Still another object of the invention is to provide a multiplex or multiunit machine wherein at least one station is common to several units.

An ancillary object of the invention is to provide an automatic press-and-blow machine which can be converted for the production of greater or lesser quantities of hollow articles per unit of time.

An additional object of the invention is to provide a machine which can convert blanks or gobs of vitreous material into bottles or like hollow articles in a small area, with a minimum of supervision and in such a way that each of a series of successively produced articles is identical with the previously or subsequently produced articles.

The machine of my invention is utilized for the production of hollow articles which consist of vitreous or plastic material.

MACHINE FOR THE It comprises a plurality of work supporting devices arranged to transport workpieces (such as gobs or blanks, parisons, and finished hollow articles) along at least one predetermined path, separate prime mover means for each work supporting device, and control means for regulating the operation of each prime mover means independently of the other prime mover means. The work supporting devices are preferably movable along an endless path, most preferably along a substantially circular path, past a plurality of stationary and/or mobile treating stations. The workpieces move into registry with successive stations during selected stages of their movement along the path.

Itwill be seen that the improved process comprises moving a plurality of workpieces along at least one predetermined path and past a plurality of treating stations at and between which the workpieces are treated to ultimately constitute hollow articles, and regulating the speed of workpieces at and between the stations as a function of the time required for treatment at and between the respective stations.

The novel features which are considered as characteristic of the invention are set forth in particular in the appended claims. The improved machine itself, however, both as to its construction and its mode of operation, together with additional features and advantages thereof, will be best understood upon perusal of the following detailed description of certain specific embodiments with reference to the accompanying drawing.

BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is a schematic partly elevation and partly vertical sectional view of a duplex press-and-blow machine which embodies the invention, the section being taken in the direction of arrows as seen from the line [-1 of FIG. 2;

FIG. 2 is an enlarged horizontal sectional view as seen in the direction of arrows from the line II-II of FIG. 1;

FIG. 3 is an enlarged fragmentary horizontal sectional view as seen in the direction of arrows from the line IIllll of FIG.

FIG. 4 is a vertical sectional view as seen in the direction of arrows from the line IV-IV of FIG. 3;

FIG. 5 is a vertical sectional view as seen in the direction of arrows from the line V-V of FIG. 3',

FIG. 6 is an enlarged fragmentary vertical sectional view as seen in the direction of arrows from the line VI-Vl of FIG. 2;

FIG. 7 is a horizontal sectional view as seen in the direction of arrows from the line VII-VII of FIG. 6;

FIG. 8 is a plan view of a mechanism which effects opening and closing of neck rings;

FIG. 9 is an enlarged bottom plan view of a holder for a neck ring;

FIG. 10 is a top plan view of the holder;

FIG. 11 is a schematic horizontal sectional view as seen in the direction of arrows from the line XI-XI of FIG. 1;

FIG. 12 is a horizontal sectional view as seen in the direction of arrows from the line XII-XII of FIG. 13 and illustrates the details of the housing for the head of the blowing unit;

FIG. 13 is an elevational view as seen in the direction of arrows from the line XIII-XIII of FIGS. 1 and 12.

FIG. 14 is a diagram showing the paths of movement of holders in the duplex machine of FIG. 1;

FIG. 15 is a partly elevational and partly sectional view of a transmission which moves the holders of the right-hand unit in the machine of FIG. 1;

FIG. 16 is a diagram showing the paths of movement of output members in the transmission of FIG. 15;

FIG. 17 is a diagram wherein curves indicating angular displacements of the output members in the transmission of FIG. 15 are plotted as functions of time;

FIG. 18 is a diagram of the control system which operates the motors for the transmission of FIG. 15;

FIG. 19 is a large-scale diagrammatic view of a detail in the structure of FIG. 18;

FIG. 20 is a diagrammatic view of a detail in the structure of FIG. 19;

FIG. 21 is a diagram illustrating the mode of operation of motors for the transmission of FIG.

FIG. 22 is another diagram illustrating certain phases in operation of motors for the transmission of FIG. 15;

FIG. 23 is a plan view of a disk combining two coded disks in the structure of FIG. 19;

FIG. 24 is a similar plan view of another disk; and

FIG. 25 is a diagram indicating the nature of impulses which are produced by the disk of FIG. 24.

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a duplex press-and-blow bottle-making machine which comprises a frame having a baseplate or bed 30. The latter resembles a pallet and is provided with openings 31 for the prongs of a forklift truck or a like transporting unit, not shown. The frame further includes two upright columns 40, 41 extending upwardly from the baseplate 30 and a crosshead 45 connecting the upper ends of the columns.

The two columns are substantially identical; therefore, the numerals which are applied in FIG. 1 merely denote the parts of one of these columns, namely, the details of the columns 40. This column 40 comprises a tubular lower section 50 which supports a horizontal table or platform 51. The upper section 55 of the column 40 extends from the platform 51 and all the way to the crosshead 45. The upper end portion of the section 55 extends into a coupling sleeve 56 of the crosshead 45 and is separably secured thereto by a coupling pin 57 or an analogous fastener. The parts 30, 40, 41, 45 form a rigid unit.

The crosshead 45 also serves as a pressure tank to supply compressed gaseous fluid to a series of pneumatic (e.g., RN/ROTAC single vane) motors which will be described later.

The lower portion of the section 55 is provided with an annular flange which defines a supporting shoulder 60 located at a level whose distance from the crosshead 45 is approximately twice the distance from the platform 51. The shoulder 60 supports the casing of a transmission 61 which will be described in detail in connection with FIG. 15. A platelike cover 62 of the transmission 61 is guided by the section 55 and serves as a carrier for four drive means each of which includes an electric motor as a prime mover (see the motor m6), a portion of a stepdown transmission (see the transmission G6) and a photoelectric signal generator (see the signal generator 1426). The signal generators form part of control means which regulate the operation of the respective electric motors.

The cover or carrier 62 further supports a downwardly extending housing or guide 69 which forms part of a blowing unit 70. The latter comprises a vertically reciprocable blowing head 71 connected with a supply conduit 72 for blowing medium and a pneumatic motor 73 which is mounted in the housing 69 and has an oscillatory output member.

The valve which controls the admission of compressed fluid to the motor is controlled by the programming system of the machine to thus regulate the speed and/or the direction of rotation of the motor. The exact construction of the motor 73 forms no part of the present invention; it suffices to say that its output member can turn back and forth through angles not exceeding 360. The output member of the motor 73 serves to move the blowing head 71 up and down in a manner to be described in connection with FIGS. 12 and 13. The controls for the motor 73 include solenoid-operated air valves or like control elements which are not shown in FIG. 1. The operation of valves is regulated by a main programming system which controls the operation of all movable parts of the machine. The programming system will be described later.

The cover or carrier 62 further supports a housing 75 which guides a plunger 76. The latter is movable up and down by a second rotary pneumatic motor 77 which is installed at the underside of the crosshead 45.

The aforementioned transmission 61 on the shoulder 60 of the column 40 comprises four orbiting output members of which only two (namely, e.g., the output member 80) are shown in FIG. 1. Each of these four output members supports a holder 81 for one of four neck rings 82 each of which includes two sections or halves (see the halves 82', 82 shown in FIGS. 9 and 10). Each section of each neck ring 82 supports an intermediate portion or carrier 83 of a composite blow mold. Depending on the position of neck rings 82, the portions 83 either support a parison (i.e., a partially finished workpiece which has undergone deformation by the plunger 76), a finished bottle 85 or another hollow article, or are empty. Each neck ring 82 forms with the corresponding holder 81 a work supporting device.

The plunger 76 is located at a pressing station S The platform 51 supports a tongs or gripper means which is adjacent to station S and whose parts or jaws are turnable on a vertical pintle 91 and receive motion from two oscillatable drive shafts 92, 92 (see also FIGS. 3 to 5). The upper end portions of the pintle 91 and shafts 92, 92 are mounted in a stiffening beam 93. The shafts 92, 92' receive motion from a stepdown transmission 95 which is driven by a rotary pneumatic motor 96. The transmission 95 and motor 96 are mounted at the underside of the platform 51. The latter is provided with an opening or cutout 99 for a carriage 100 which supports a blank mold 101. The carriage 100 is caused to perform linear movements (up and down) by a first driving or lifting unit 102 which receives motion from a rotary pneumatic motor 103 (FIG. 2). In addition, the carriage 100 is rotatable about a vertical axis by means of a second driving or oscillating unit 104 which receives motion from a rotary pneumatic motor 105 (see FIG. 2). The unit 104 can move the blank mold 101 in directions at right angles to the latters vertical axis between a blank-receiving position and a second position of registry with the plunger 76.

The first driving or lifting unit 102 comprises a housing which is suspended on the platform 51 and carries the motor 103 and accommodates a vertical guide rod 111. The guide rod 111 supports a hub or sleeve 113 which supports the carriage 100 and is engaged by a fork 112 driven by the motor 103. A similar sleeve or hub 114 is mounted on a shaft 115 of the blank mold 101 and is turnable by the aforementioned second driving or oscillating unit 104 (see FIG. 2).

The platform 51 further supports a gripper means or tongs for blow molds. This tongs 120 is adjacent to the blowing station S which accommodates the aforementioned blowing unit 70. The portions of tongs 120 are turnable on a vertical pintle 121 and receive motion from two vertical drive shafts (only shaft 122 shown in FIG. 1) which are similar to the drive shafts 92, 92' for the tongs 90. The tongs 120 supports the lower sections or halves of a blow mold 123. When the blow mold 123 closes, its lower sections engage a vertically movable blow mold bottom plate 124 and the portions 83 in a neck ring 82. The bottom plate 124 is movable up and down by a driving or lifting unit 125 which is shown in greater detail in FIGS. 6 and 7. This lifting unit 125 receives motion by way of its pin 126 and is supported by a plate 130 which is secured to the platform 51 by a bracket 131. The drive shafts 122 for the tongs 120 receive motion from a stepdown transmission which is driven by a rotary pneumatic motor 136. The parts 135, 136 are connected to each other and are suspended at the underside of the platform 51.

The heretofore described parts of the duplex machine shown in FIG. 1 constitute a fully operative assembly which is capable of producing hollow articles of glass or synthetic plastic material. The right-hand portion of the duplex machine shown in FIG. 1 is provided in order to raise the output and the parts of this right-hand portion are constructed and assembled in the same way as the heretofore described parts with the exception that the pressing station S, is common to both halves of the duplex machine. The transmission on the right-hand column 41 of FIG. 1 performs the same functions as the transmission 61 on the column 40. The blowing station in the right-hand unit of the machine is shown at S It is clear, however, that each unit of the duplex machine can be provided with a separate pressing station corresponding to the station S It is equally within the purview of my invention to employ two pressing stations 8, and a common blowing station In order to enhance the stability of the machine frame, the platform 51 may be supported by three or more columns. FIG. 1 shows a third column 155 and Fig. 2 shows several additional columns 156, 157, 158, 159, 160.

The left-hand portion of FIG. 2 shows a rotary pneumatic motor 1600 which drives the blow mold bottom plate 124. This FIG. 2 further shows the details of the oscillating unit 104 for the carriage 100 of the blank mold 101. The output shaft of the motor 105 drives an eccentric pin 162 connected to one end of a connecting rod 163. The other end of the connecting rod 163 is coupled to a pin 164 on one arm of a lever which is rockable on a shaft 165. The other arm of the lever is bent downwardly as shown in FIG. 1 and is rigid with the sleeve 114. When the pin 162 rotates, the carriage 100 turns about the axis of the shaft 165 from the position shown in FIG. 2 to a second position in which the blank mold 101 receives a gob or blank from a conventional gob feed, not shown. The feed includes a funnel which receives gobs from a source of plasticized vitreous or synthetic plastic material. During movement to second position, the blank mold 101 turns about the shaft 165 in a counterclockwise direction, as viewed in FIG. 2. The opening 99 in the platform 51 is configurated in such a way that it permits oscillatory movements of the carriage 100 for the blank mold 101. When the blank mold 101 receives a gob, it is remote from the pressing station 5,, i.e., it does not register with the plunger 76.

The endless circular paths 170, 171 along which the axes of the neck rings 82 travel are shown in FIG. 2 by phantom lines. The directions of travel of neck rings are denoted by arrows 172, 173.

The tongs 90 for blank molds 101 and the tongs 120 for blow molds 123 are preferably of identical size and shape to simplify maintenance, repair and replacement. The tongs 90 is illustrated in FIGS. 3 to 5. The jaws of the tongs 90 are shown at 90 and 90". The transmission 95 receives motion from the output shaft 175 of the motor 96 (FIG. and includes a spur gear 176 which is keyed to the shaft 175. The gear 176 meshes with an identically dimensioned intermediate gear 177 which meshes with a gear 179 on the drive shaft 92'. The gear 176 is further in mesh with a gear 178 on the drive shaft 92. The gears 178, 179 are identical; therefore the shafts 92, 92' are driven at the same speed and through identical angles but in opposite directions. These shafts are splined and carry radially extending arms 180, 180 which are coupled with links 181, 181 and these links are respectively coupled to the jaws 90", 90' of the tongs 90. The arms 180, 180 are adjustable in the axial direction of the shafts 92, 92. When the output shaft 175 rotates back and forth, the jaws 90', 90" move between the solid line closed positions and the phantom line open positions shown in FIG. 3.

FIG. 4 shows a neck ring 82 in axial alignment with the tongs 90. The pintle 91 enhances the stability of the jaws 90', 90 and the position of these jaws can be adjusted in the axial direction of the pintle 91 by changing the position of two stop rings 190, 191. Such adjustment must be accompanied by commensurate adjustment of arms 180, 180' relative to the drive shafts 92, 92. The arms 180, 180 have slotted hubs (see FIG. 3) which can be fixedly secured to the respective drive shafts by screws or bolts 192 indicated in FIG. 4. The adjustability of the distance between the neck ring 82 and tongs 90 renders it possible to utilize different sizes of molds and/or neck rings.

FIG. 5 shows that the transmission 95 occupies very little room in the space between the motor 96 and the underside of the platform 51.

FIG. 6 shows the aforementioned plate 130 which is secured to the platform 51, together with the rotary pneumatic motor 1600. by means of suitable brackets or the like which are not specifically identified in the drawings. The plate 130 supports the lifting unit for the blow mold bottom plate 124, and this lifting unit comprises a slidable rod 195 whose upper end is connected to the bottom 124. The rod 195 is reciprocable in a bearing sleeve 196 which is fixedly mounted in the plate 130. The lower end portion of the rod 195 extends beyond the sleeve 196 and is connected to a crosshead 198 by way of a clamping screw 197. The crosshead 198 is adjustable lengthwise of the rod 195 and carries the aforementioned pin 126. In order to enhance the accuracy of reciprocatory movement of the rod 195, the crosshead 198 is reciprocably guided by a vertical post 199 which is secured to and extends downwardly from the plate in parallelism with the rod 195.

The drive for the pin 126 comprises a connecting rod 201 which is connected to a crank pin 200. The latter is oscillatable back and forth as indicated by double-headed arrow 202.

Upon completed blowing of an article at the blowing station S or S the article is advanced to a transfer station S or 5;, (FIG. 14). When it reaches the station S or S the neck ring 82 must open to release the finished article and to allow such article to advance with a further conveyor located below the level of the neck ring. The opening and subsequent closing of neck rings is effected mechanically in a manner as shown in FIG. 8. This illustration shows a star-shaped switching member 205 in two different extreme positions. FIGS. 9 and 10 show the switching member 205 together with an associated neck ring holder 81. The sections 82, 82" of the neck ring 82 are reciprocable along shafts 206, 207. The switching member 205 has a shaft 209 which extends through the neck ring holder 81 and is connected with a switching plate 208. The plate 208 has two projections 210, 211 each of which carries an eye provided on one of two leaf springs 212, 213 which are respectively secured to the neck ring sections 82', 82". The configuration and mounting of leaf springs 212, 213 is such that they can hold the switching member 205 in a closing position (FIG. 9) or in an opening position (FIG. 10). In each of its positions, the switching member 205 is safely locked by the springs 212, 213. This is achieved by mounting the springs in such a way that the axes of projections 210, 211 are caused to move beyond a horizontal plane including the axis of the shaft 209 in each extreme position of the member 205.

Each switching member 205 carries four rollers 215, 216, 217, 218. These rollers constitute followers and can track the faces of fixed cams to thereby cause movement of neck ring sections 82', 82" with reference to each other. The cams are shown at 220, 221, 222 and 223 (FIG. 8) and are affixed to the frame of the machine. When the switching member 205 advances in the direction indicated by arrow 230 (FIG. 8), the axis of its shaft 209 travels along the line 231, i.e., the holder 81 cannot move up and down.

When it assumes the position shown in the left-hand part of FIG. 8, the switching member 205 maintains the neck ring 82 in closed position (FIG. 9). During movement of the switching member 205 to such closing position, the roller follower 218 engages first the cam 220 and thereupon also the cam 221. While the follower 218 is being guided by these cams, its axis travels along the phantom line path 233. The tongs 82 is open (FIG. 10) when the switching member 205 reaches the position shown in the right-hand part of FIG. 8. During travel between the two positions shown in FIG. 8, the switching member 205 completes one-half of a revolution about the axis of the shaft 209 by turning in a clockwise direction. The axes of rollers followers 215, 216, 217 travel along the phantom line paths 234, 235, 236. When the switching member 205 moves back toward the position shown in the left-hand part of FIG. 8, its roller follower 215 is guided by the cams 222, 223. The switching member then turns in a counterclockwise direction.

FIGS. 9 and 10 show that the neck ring holder 81 is provided with springy cushions 240 which extend beyond its outline. These cushions abut against similar cushions 240 of other holders 81 if two or more holders happen to move close to each other.

Referring now to FIG. 11, there are shown certain details of the portion of the duplex machine which embodies the invention. Each of the two individual machines is provided with four separate transmissions each of which operates one of four neck ring holders 81. FIG. 11 shows the transmission G of the right-hand machine and the transmission G of the left-hand machine. The details of such drives will be described with reference to FIG. 15.

FIG. 1 1 further shows the positioning of housings 69, 69 for the heads of the blowing units and the housing 75 for the plunger 76. FIGS. 12 and 13 show the details of parts in the housing 69 for the head 71 of the blowing unit 70. The other housing 69 is of similar design. As shown in FIGS. 12 and 13, the housing 69 is affixed to the underside of the cover 62 by screws 250. The.interior of the housing 69 is provided with two vertical ribs 251, 252 supporting carriers 254, 255 which are affixed thereto by screws 253. Each of the carriers 254, 255 supports two pairs of rollers 256, 257 in such a way that each pair of rollers on the carrier 254 is located directly opposite one pair of rollers on the carrier 255. The axes of rollers in each pair of rollers make an angle of 90 and their peripheral surfaces track the adjoining sides of a vertically reciprocable tube 260 of rectangular outline. The tube 260 constitutes an extension of the blowing head 71. The aforementioned supply conduit 72 for blowing medium terminates at the upper end of the tube 260 and is coupled to a pressure conduit 262 which extends axially through the tube 260 and is centered by ribs or fins 261. The pressure conduit 262 is connected to-a supply conduit 263 at the lower end of the tube 260.

The tube 260 further supports a vertically adjustable clamp 267 which is secured thereto by screws or bolts 264, 265. The clamp 267 carries a pin 269 which is connected with the lower end of a connecting rod 270. The latter is driven by the motor 73 to move the tube 260 up and down. The upper end position of the tube 260 is shown in FIG. 13 by phantom lines, as at 260'.

FIG. 14 illustrates schematically the paths 170, 171 for the centers of the neck rings 82 in both machines of the duplex structure shown in FIGS. 1 and 11. The manner in which a gob or blank is converted into a finished article will be described with reference to the left-hand machine of FIG. 14. The numeral 300 denotes a path along which the blank mold 101 moves while it receives a gob from the funnel of the gob feed. During such feeding, the blank mold 101, portions 83 and the corresponding neck ring 82 advance toward the center of the tongs 90 at the pressing station SI. On entry of such parts into the station S1, the tongs 90 grips the portions 83 and the blank mold 101 and yieldably centers these parts in the corresponding supporting elements of the machine. The plunger 76 penetrates into the blank mold 101 and converts the gob into a parison. The tongs 90 thereupon opens and the blank mold 101 moves downwardly and advances from the path 300 to the gob feeding station 301. During travel along the stretch 302, the neck ring 82 is accelerated from zero speed to normal speed (stretch 303), and then maintains such normal speed until it enters the braking or decelerating stretch 304 where its speed decreases to zero when it reaches the blowing station S2. The time required for the neck ring 82 to advance along the stretches 302, 303, 304 is selected in such a way that it suffices to reheat the parison. The purpose of reheating and of eventual additional treatment along the stretches 302-304 is to control the temperature in portions of the parison, i.e., the temperature in various layers of the parison wall must be brought to a predetermined optimum value.

When the neck ring 82 enters the blowing station S2, the blow mold bottom plate 124 is moved upwardly and the tongs 120 for the lower blow mold sections 123 (which are suspended therein) grips the portions 83 and the bottom plate 124 to properly center such parts. The blowing head 71 engages the centers of the portions 83 and converts the parison into a finished blown article 85, e.g., a glass bottle. The tongs 120 thereupon opens and the bottom plate 124 returns to its lower end position.

During travel along the stretch 305 of the path 170, the neck ring 82 is accelerated from zero speed to normal speed (when it reaches the stretch 306) and is thereupon decelerated along the stretch 307 back to zero speed when it reaches the pressing station S1. During travel along the stretch 306, the speed of the neck ring 82 remains substantially unchanged. This also applies for travel of the neck ring through the transfer station S3 where the neck ring travels above a takeoff conveyor 308. When it reaches the station S3, the neck ring with a finished article therein is located above the central portion of the conveyor 308. The neck ring opens and allows the article 85 to descend onto the conveyor 308 which transports it to a lehr (cooling oven) in the direction indicated by arrow 309. During travel along that portion of the stretch 306 which is located downstream of the transfer station S3, the neck ring 82 remains open (see FIG. 10) and its portions 83 can be treated, e.g., cleaned and lubricated. The cams 222, 223 of FIG. 8 then cause the neck ring to close (FIG. 9). Closing of the neck ring can take place along the last part of the stretch 306 or during travel along the stretch 307, as long as it is completed when the neck ring returns to the pressing station S1.

The manner in which the neck rings travel along the stations S1, S2 and S3 in the right-hand machine of FIG. 14 is analogous. However, the travel of neck rings in the two machines is controlled in such a way that a neck ring which travels along the path 170 enters the pressing station S1 when a neck ring which travels along the path 171 leaves the pressing station, and vice versa. Thus. the operating cycles of the two machines are phase-displaced with reference to each other because the two machines or units of the illustrated duplex machine receive gobs at a single pressing station S1.

The distance between the neck rings 82 and the conveyor 308 is preferably adjustable. This conveyor may comprise an endless belt which travels at the speed at which the holders 81 travel along the stretch 306.

FIG. 15 illustrates the details of the transmission which is shown in the right-hand part of FIG. 1. The column 41 has a portion or section 315 provided with a shoulder 316 (corresponding to the shoulder 60 on the section 55 of the column 40 shown in FIG. 1) which supports a distancing ring 317 supporting a platform 318 for cams (corresponding to the cams 221L223 of FIG. 1) and for a container (not shown) which accommodates lubricant for the portions 83. The platform 318 further supports a second distancing ring 319 which abuts against the lower end of a hub 320 extending from a bottom wall 321 forming part of the case for the transmission 150. The hub 320 is held against rotation by a key 322 which extends into an axially parallel groove 323 of the section 315. The bottom wall 321 carries a stack of internal gears 324, 325, 326, 327 which are separated by disks 328, 329, 330. Each of these disks has a hub which surrounds the section 315. A similar hub is provided on a top wall 331 which is located above the topmost gear 327. All of the hubs are accurately centered on the section 315 against uncontrolled radial movement. These hubs are spaced axially from each other by distancing elements 335 which are disposed between the disks 328, 329, 330, between the disk 328 and bottom wall 321 and between the disk 330 and top wall 331. The transmission 150 further comprises annuli of spherical rolling elements 339 which are interposed between superimposed parts (such as between the bottom wall 321 and adjoining gear 324). The rolling elements 339 engage tracks provided by surfaces which are inclined with reference to the axis 338 of the column 41. Such inclination of surfaces which form the tracks insures satisfactory guidance of rolling elements 339 against radial movement. Washers which are installed between the distancing elements 335 and the adjoining parts insure requisite axial positioning of rolling elements 339.

Each of the gears 324-327 has a radially outwardly extending output member 340 corresponding to the output member 80 of FIG. 1, and each of these output members 340 carries one of the holders 81 for neck rings 82. The length of each of 

1. In a machine for the production of hollow articles consisting of vitreous or synthetic plastic material, a combination comprising a plurality of treating stations arranged spaced from each other along an endless predetermined path; means provided at said stations for treating workpieces of such material to ultimately transform said workpieces into hollow articles, a plurality of work-supporting devices arranged to transport workpieces along said path and into registry with said means at said treating stations; separate prime mover means for each of said work-supporting devices; and control means for controlling the operation of each prime mover means independently of the other prime mover means for regulating the movement of the worksupporting device at and between said stations as a function of the time required for treatment of the workpieces carried by the respective work-supporting device at and between the respective station.
 2. A combination as defined in claim 1, wherein said treating stations comprise at least one pressing station for pressing a gob of such Material into a parison and at least one blowing station spaced in the direction of movement of said work-supporting devices from said pressing station for blowing the parison produced in said pressing station into a finished hollow article.
 3. A combination as defined in claim 1, wherein said predetermined endless path is a substantially circular path and including means connecting each of said prime mover means to a respective one of said work-supporting devices to orbit the latter along said circular path.
 4. A combination as defined in claim 1, wherein said work-supporting devices are disposed in groups arranged to transport workpieces along separate paths, a plurality of said treating stations being arranged along each of said paths.
 5. A combination as defined in claim 1, and further comprising drive means for said treating means, and programming means for said control means and said drive means.
 6. A combination as defined in claim 1, wherein at least one of said stations is stationary and wherein said prime mover means are arranged to arrest the respective work supporting devices at least at one of said stations.
 7. A combination as defined in claim 1, wherein at least one of said stations is a mobile station and further comprising means for moving said one station in synchronism with said work-supporting devices.
 8. A combination as defined in claim 7, wherein each of said work supporting devices is arranged to register with said one station during travel along a predetermined portion of said path.
 9. A combination as defined in claim 1, further comprising at least one stationary pressing station adjacent to said path, means at said station for converting blanks into parisons constituting one form of said workpieces, a stationary second station adjacent to said path downstream of said pressing station and means at said second station for converting parisons into finished hollow articles, each of said work-supporting devices comprising a carrier for workpieces.
 10. A combination as defined in claim 9, wherein the means at said second station comprises a mobile blow mold bottom member, a multisection blow mold, gripper means carrying said blow mold for coupling successive work supporting devices with parisons therein to said bottom member, and a blowing unit for admitting a blowing medium into parisons to thus convert such parisons into finished hollow articles while the corresponding work supporting devices are engaged by said blow bold.
 11. A combination as defined in claim 9, wherein the means at said stations include movable components and separate driving units for such movable components.
 12. A combination as described in claim 1, further comprising transmission means interposed between said prime mover means and said work-supporting devices.
 13. A combination as defined in claim 12, wherein said transmission means is a stepdown transmission.
 14. A combination as defined in claim 13, wherein said transmission comprises a plurality of rotary output members each supportingly connected with one of said work-supporting devices.
 15. A combination as defined in claim 14, wherein said transmission further comprises gears each connected with and arranged to move one of said output members.
 16. A combination as defined in claim 15, wherein said gears are internal gears and said output members extend outwardly from the respective gears.
 17. A combination as defined in claim 4, wherein each of said separate paths has at least one common point with one other of said separate paths.
 18. A combination as defined in claim 16, wherein said internal gears are arranged to rotate about a common axis and wherein said transmission further comprises separating means interposed between said gears.
 19. A combination as defined in claim 18, wherein said separating means include two outermost separating means and said transmission further comprises a case including said outermost separating means.
 20. A combination as defined in claim 18, wherein said transmission further comprises centering means extending axially through said gears and said separating means, and distancing means interposed between said separating means.
 21. A combination as defined in claim 18, wherein said separating means comprises a pair of outermost separating means and wherein said transmission further comprises clamping means connecting said outermost separating means against relative movement axially of said gears.
 22. A combination as defined in claim 15, wherein said gears are coaxial and said transmission further comprises means for locating said gears against radial and axial movement with reference to each other.
 23. A combination as defined in 22, wherein said locating means comprises distancing and clamping elements and wherein said gears are internal gears which surround said elements.
 24. A combination as defined in claim 16, wherein said prime mover means include a prime mover means for each of said gears and wherein said transmission further comprises pinions each driven by one of said prime mover means and each meshing with one of said gears.
 25. A combination as defined in claim 14, wherein said output members are arranged to orbit about a common axis and are movable angularly with reference to said common axis and spaced from each other in the direction of movement, said work supporting devices being connected with the respective output members in such a way that they transport workpieces in a common plane.
 26. A combination as defined in claim 1, wherein each of said work-supporting devices comprises a composite neck ring having sections movable with reference to each others between open and closed positions, and further comprising means for moving the sections of successive neck rings with reference to each other while the corresponding work supporting devices travel along at least one predetermined portion of said path.
 27. A combination as defined in claim 1, further comprising a transfer station adjacent to said path downstream of said treating stations, and means for receiving finished articles from said devices at said transfer station.
 28. A combination as defined in claim 27, wherein the means for receiving finished articles comprises conveyor means located at a level below said path.
 29. A combination as defined in claim 28, wherein said conveyor means is arranged to travel at said transfer station at the same speed and in the same direction as the work-supporting devices which move past said transfer station.
 30. A combination as defined in claim 29, wherein said work-supporting devices comprise neck rings having sections movable between open and closed positions in which they respectively support and release the respective workpieces, and further comprising means for moving said sections to open positions during travel of the respective neck rings past said transfer station.
 31. A combination as defined in claim 4, wherein said devices are disposed in two groups and said paths have a common portion, one of said treating stations being adjacent to the common portion of said paths.
 32. A combination as defined in claim 31, wherein the means at said one station comprises means for converting blanks into parisons.
 33. A combination as defined in claim 31, wherein the means at said one station comprises means for converting parisons into finished articles.
 34. A combination as defined in claim 31, further comprising frame means including a base member, a pair of columns extending upwardly from said base member, and a crosshead connecting the upper ends of said columns, each of said groups of work-supporting devices being arranged to orbit about one of said columns.
 35. A combination as defined in claim 5, wherein said programming means comprises a programming unit or a plurality of programming units, one for each of said stations, for programming the treatment at each of saiD treating stations, and logic circuit means for interconnecting said programming unit or units with said control means in such a manner that each workpiece is moved to the subsequent treating station along said path after completion of treatment at the preceding treating station.
 36. A combination as defined in claim 35, wherein each of said separate prime mover means comprises a direct current motor with regulatable rotational speed.
 37. A combination as defined in claim 35, further comprising synchronizing means for synchronizing the operation of said plurality of programming units.
 38. A combination as defined in claim 35, wherein said control means comprises a plurality of separate control means, one for each of said prime mover means, and wherein each of said separate control means comprises position signal generating means for generating position signals each signifying that the corresponding devices has reached a predetermined position along said path.
 39. A combination as defined in claim 38, wherein said position signal generating means comprise photoelectric means.
 40. A combination as defined in claim 39, wherein each of said prime mover means comprises an electric motor having a rotary shaft and each of said photoelectric means comprises a source of light, one on a plurality of disks having translucent portions coupled to the shaft of the respective motor and located in the path of light from said light source in such a manner that light transmitted through a disk is a function of the angular position of the respective shaft, and photoelectric transducing means for receiving the light transmitted through said disks and for generating electrical position signals in correspondence thereto.
 41. A combination as defined in claim 40, wherein each of said motors is a shunt-wound direct current motor having a speed that varies as a function of armature voltage, and wherein each of said control means further comprises a source of reference voltage for supplying a reference voltage to the armature of the respective motor for causing the motor to rotate at rated speed, and for decreasing said reference voltage in response to selected ones of said position signals to cause the motor to decrease its speed when approaching a stationary station.
 42. A combination as defined in claim 41, further comprising means for limiting the armature current in such a manner that no excessive acceleration can take place.
 43. A combination as defined in claim 41, wherein said source of reference voltage comprises digital counting means set to a predetermined number and means for counting back on said counting means in response to said selected ones of said position signals.
 44. A combination as defined in claim 43, wherein said source of reference voltage constitutes first positioning means and further comprising fine positioning means and a switching unit for switching from said source of reference voltage to said fine positioning means in response to the position signal causing the last countback on said counting means.
 45. A combination as defined in claim 44, wherein the position signal generated within a predetermined small angle immediately preceding the desired positions of the workpiece has a trailing edge starting at a positive polarity and ending at a negative polarity, and wherein said fine positioning means comprises means for furnishing said electrical position signals generated within said predetermined small angle.
 46. A combination as defined in claim 45, further comprising regulating means connected between said switching means and the respective motor.
 47. A combination as defined in claim 46, wherein said regulating means comprise means for comparing a voltage proportional to the actual motor speed to a variable reference voltage furnished via said switching means and generating an error voltage as a function of the difference between said voltages; and output means for supplying voltage to said motor in respOnse to said error voltage in such a manner that said error voltage is reduced toward zero.
 48. A combination as defined in claim 47, wherein said output means comprise an output stage having a rectifier whose output voltage for four-quadrant operation is settable by means of the phase cut-in method. 